Reciprocally operable air motor and exhaust valve therefor



Oct. 4, 1966 c. c. KINKER 3, 7

RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR Original Filed Jan. 2, 1963 15 Sheets-Sheet l INVENTOR. CLARENCE C. KINKER C. C. KlNKER Oct. 4,- 1966 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR l5 Sheets-Sheet 2 Original Filed Jan. 2, 1963 INVENTOR. CLARENCE C. KlNKER THEREFOR l5 Sheets-Sheet 5 INVENTOR. CLARENCE C. KINKER C- C. KINKER Oct. 4, 1966 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE Original Filed Jan. 2, 1963 C. C. KINKER Oct. 4, 1966 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR l5 Sheets-Sheet 4 Original Filed Jan. 2, 1963 FIG, 4

INVENTOR. CLARENCEC. KINKER C. C. KINKER Oct. 4, 1966 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR 15 Sheets-Sheet 5 Original Filed Jan. 2. 963

"TOR. CLARENCE C.KN KER Oct. 4, 1966 c. c. KINKER 3,276,475

RECIPROGALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR Original Filed Jan. 2, 1963 15 Sheets-Sheet 6 INVENTOR. .IlllffffffIfII: CLARENCE C. KINKER c. c. KINKER 3,276,475

ND EXHAUST VALVE THEREFOR Oct. 4, 1966 RECIPROCALLY OPERABLE AIR MOTOR A 15 Sheets-Sheet 7 Original Filed Jan. 2, 1963 INVENTOR. CLARENCE C.& \N KER C. C. KINKER Oct. 4, 1966 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR l5 Sheets-Sheet 8 Original Filed Jan. 2, 1965 INVENTOR, CLARENCE C.K\NJKER mvd ,7 NmNJ C. C. KINKER Oct. 4, 1966 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR l5 Sheets-Sheet 9 Original Filed Jan. 2, 63

INVENTOR. CLARENCE C KINKER c. c. KlNKER 3,276,475

RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR Oct. 4, 1966 15 Sheets-Sheet 10 Original Filed Jan. 2, 63

{NVENTOR CLARENCE C. KENKER Oct. 4, 1966 c. c. KINKER 3,276,475

RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR Original Filed Jan. 2. 963

15 Sheets-Sheet ll INVENTOR. CLARENCE C. KINKER C. C. KINKER Oct. 4, 1966 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR l5 Sheets-Sheet l2 Original Filed Jan.

INVENTOR. CLARENCE C, KINKER C. C. KINKER Oct. 4, 1966 RECIPROCALLY OPERABLE AIR NOTOR AND EXHAUST VALVE THEREFOR l5 Sheets-Sheet 13 Original Filed Jan. 2. 1963 {NVENTOR CLARENCE C. KINKER c. c. KINKER 3,276,475 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR Oct. 4, 1966 15 Sheets-Sheet 14.

Original Filed Jan. 2. 63

I N VE NTOR.

R E K W C E W A L c C. C. KINKER Oct. 4, 1966 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR l5 Sheets-Sheet 15 Original Filed Jan. 2, 1963 MSW w a m;

INVENTOR. CLARENCE QKINKER United States Patent 3,276,475 RECIPROCALLY OPERABLE AIR MOTOR AND EXHAUST VALVE THEREFOR Clarence C. Kinker, Manitou Beach, Mich., assignor to Owens-Illinois, Inc., a corporation of Ohio Original application Jan. 2, 1963, Ser. No. 249,025, now Patent No. 3,224,307, dated Dec. 21, 1965. Divided and this application July 19, 1965, Ser. No. 472,862

1 Claim. (Cl. 137-6255) This application is a division of my co-pending application, Serial No. 249,025, filed January 2, 1963, now US. Patent 3,224,307.

This invention relates generally to a method and apparatus for handling sheet material and more particularly to a method and apparatus for processing large panels of cardboard or like material to slit and cut them to any desired size with no manual handling required except loading and unloading.

In the manufacture of corrugated cardboard carton separators, such as are used in packaging various types of glassware, it is customary to start with relatively large panels of cardboard and cut the panels into separators of the desired size. Typically this involves loading the large panels onto a conveyor leading to a plurality of slitters which cut the large sheets into a plurality of sections or blanks of the height required for the finished separator. These long blanks are then manually removed from the slitter and fed into a saw which cuts them to the proper length and notches them. From the saw the separators are placed on pallets for temporary storage.

In the cutting operation described above, typically there is an operator to load the large sheets to the slitter. A second operator removes the long slitted blanks from the slitter and feeds them to the saw, while a third operator removes them from the saw. Problems are presented in the above operation in that it is impossible to properly coordinate the work load among the various steps in the operation. For example, it is possible for the slitter to turn out the long blanks much faster than the saw can process them. As a result, the speed of the saw limits the speed with which the slitter can operate. This in turn leaves the slitter loader operator to stand idle for long periods of time in each cycle. Such inefliciency, of course, greatly increases the cost of processing.

The present invention eliminates this inefficiency by providing completely automatic sheet handling mechanism from the time the sheets are loaded to the slitter to the time the cut-to-size separators are removed from the saw.

Accordingly, it is an object of this invention to provide a completely automatic ap aratus for handling large sheets of material as they are trimmed to desired uniform sizes.

Another object of this invention is to provide apparatus for stacking long slitted blanks into bundles and unloading the bundles to a mechanism adapted to reorient single bundles into position for cutting.

An additional object of this invention is to provide apparatus for moving said reoriented bundles to a saw for cutting to proper length.

A further object of this invention is to provide a novel method for handling sheet material during its cutting to smaller sizes.

Still another object of this invention is to provide an exhaust valve for controlling deceleration and stoppage of air motors powering the movement of conveyors.

A more detailed description and a better understanding of this invention may be gained from the following description taken in conjunction with the drawings in which:

FIG. 1 is a perspective view showing the apparatus of this invention.

FIG. 2 is an elevational view of the unloader portion of the apparatus of this invention.

FIG. 3 is a plan View of the unloader.

FIG. 4 is a cross-sectional view taken through line 4-4 of FIG. 2.

FIG. 5 is a cross-sectional view taken through line 5-5 of FIG. 3.

FIG. 6 is a plan view of the uprighter.

FIG. 7 is an elevational view of the uprighter.

FIG. 8 is a detailed plan view of one end of the uprighter showing the mechanism for turning the bundles and for removing the edge-turned bundles from the uprighter.

FIG. 9 is the end elevational view of the mechanism shown in FIG. 8

FIG. 10 is a perspective view of the uprighter adjusting mechanism.

FIGS. 11 and 12 are detailed elevational views of the clamping mechanism which transfers edge-turned bundles to the saw.

FIG. 13 is a perspective view of the double port exhaust valve of the present invention.

FIG. 14 is a cross-sectional view taken through line 14-14 of FIG. 13.

FIG. 15 is a cross-sectional View taken through line 1515 of FIG. 13.

FIG. 16. is a schematic view of the hydraulic systems used to operate the apparatus of the present invention.

In brief, and with reference to FIG. 1, this invention comprises a conveyor 10 for feeding single panels of sheet material through a slitter 20 which may be adjusted to slit the large sheet into blanks of any desired width. The slitted blanks are fed from the slitter to an underfeed stacker 36} where the blanks are stacked into bundles. At the end of the underfeed stacker 30 is an unloader 40 having a backstop which temporarily stops each of the slitted blanks and thereby aligns the ends of the blanks. After a predetermined number of blanks have been stacked, the backstop is caused to move away from the slitters in the direction of slitting. The underfeed stacker 30 which moved the blanks to the backstop causes the stacked bundles to move with the backstop onto the un loader 40. As the bundles enter the unloader, they are engaged and supported by a plurality of transversely disposed members mounted for operation with the backstop. When the backstop reaches the end of its longitudinal stroke, a pusher plate, mounted for transverse movement with respect to the backstop movement, pushes the bundles off the transverse supporting members and onto an uprighter 50 which is adapted to successively turn each bundle so that each blank thereof rests on its longitudinal edge. From the uprighter 50, the edgeturned bundles are fed longitudinally with respect to their length to a clamp 60 which supports and moves the edgeturned bundles to a saw where they are cut to desired length.

The saw mechanism is of known construction and does not constitute part of the present invention. Although it may be used with many types of saws, the apparatus of the present invention is specifically adapted for use with the saw described in US. Patent No. 2,855,009 to McOormick, assigned to the assignee of the present invention.

Referring to the specific details, the conveyor 10 feeds large panels 26 of cardboard or similar sheet material to the slitter 20 which slits the panels into a plurality of blanks 26a-e of desired widths. The conveyor 10 serves to move the panels 26, either singly or in stacks of any desired height, from a loading area to the slitter 20. The panels 26 are fed singly through the slitter 20. Ac-

cordingly, when the sheets are on the conveyor in stacks, it is necessary to provide means for removing single panels from the stack to the slitter 20. Such means include a pair of brackets 12 supported by a structural cross-member (not shown). The lower end of each of the brackets 12 is positioned above the conveyor 10 a sufficient distance to permit only a single panel 26 of cardboard to pass thereunder. A fluid pressure cylinder 14 is mounted on each of the brackets 12. Pivotally connected to the free end of the piston rod of each cylinder 14 is a rocker member 15. Each rocker member 15 has an upstanding leg 15a and an outwardly extending leg 15b at substantially right angles to each other. Each of the rocker members 15 is pi-votally supported on a shaft 16 at the'juncture of the two legs 15a and 15b. The shafts 16 may be supported by any desired means to the brackets 12. Each of the outwardly extending legs 15b has a downwardly extending arm 17 appended to its free end. In FIG. 1 the free ends of the respective cylinder piston rods are retracted so that the lower ends of the downwardly extending arms 17 are close enough to the conveyor to prevent the single panel 26 of cardboard which has passed under the brackets 12 from passing thereunder. Upon activation of cylinders 14, the free ends of the respective piston rods are extended slightly, thereby causing the downwardly extending arm 17 of the rocker members 15 to be pivotally moved upward to thereby permit single panel of cardboard 26 to pass thereunder and through the slitters 20. After a predetermined number of panels 26 has passed under the downwardly extending arm 17 of the rocker member 15, the cylinders are again activated by any preferred counting means to retract their respective piston rods to lower the downwardly extending arm 17 and prevent additional panels from passing to the slitter 20.

The slitter is known in the art and requires no additional description except to note that it may be supplied with any number of knives depending on the number of blanks to be cut from a single panel 26 of cardboard. Also, the spacing between the knives may be varied to cut blanks of any desired width. The slitter in FIG. 1 is shown with five pairs of knives 19a, 19b, 19c, 19d and 19e, respectively. Assuming that the knives 19a merely trim any excess from the panel 26 and the knives 1% cut a full width blank, the slitter 20 as shown in FIG. 1 will cut five blanks from each panel of cardboard. These blanks have been designated 26a, 26b, 26c, 26d and 26e, respectively. The blanks pass between a pair of rollers 22 which assist in pulling them through the slitter 20.

As each of the respective blanks leaves the slitter 20 it travels to the underfeed stacker 30. The edge of the underfeed stacker is aligned with the first pair of knives 19a so that any excess which is trimmed from the panel 26 will fall harmlessly to a salvage collector.

Underfeed stacker The underfeed stacker 30 comprises a plurality of endless belts 23 supported on continuously rotating rollers 24 powered by any desired means (not shown). A center roller 25 is positioned between the end rollers 24 and is elevated above the plane defined by the respective end rollers 24. The roller 25 thus causes each of the belts 23 to have a hump about which each of the blanks pivots as it is moved from the slitter 20. At the end of the belts 23 is positioned a backstop 34 of the unloader. As the ends of the respective blanks 2611-2 contact the backstop 24, the blanks are caused to stop and remain stationary even though the belts 23 continue to move. As will become clear from the following, each successive set of blanks 26a-e is fed underneath the preceding set to thereby stack the respective sets.

The position of the center roller 25 between the two end rollers 24 may be adjusted, its location depending upon the length of the blanks 26ae. Thus, the distance between the point of contact of the backstop 34 and the center of the roller 25 must be greater than one-half the length of the blanks so that, as the leading edges of the blanks approach the backstop, the blanks will pivot around the center roller 25 and be supported on the portion of the belts between the center roller 25 and the backstop 34. On the other hand, such distance must be less than the overall length of each blank. This is necessary so that the trailing portion of the blanks 26ae overhangs the portion of the belts between the center roller 25 and the slitter 20. By such positioning, when one set of blanks 26ae is stopped by the backstop 34, the trailing ends of said blanks will be held above the surface of the belts 23 because of the hump caused by the roller 25. When the next set of blanks is transferred from the slitter 20 to the belts 23, their respective leading edges will contact that portion of the belts between the roller 25 and the slitter 20, thereby causing such leading edges to be directed under the raised trailing edges of the preceding blanks. The belts 23 may be surfaced with any preferred material which will cause the friction between the belts 23 and the blanks to be greater than the friction between the respective blanks. As a result, each succeeding set of blanks is caused to progress forward to the backstop underneath the preceding sets of blanks. In a similar manner successive sets of blanks are caused to be fed under the preceding sets of being-stacked blanks until the predetermined number passing under the brackets have been stacked.

Unloader Referring now to FIGS. 2, 3 and 4, there is shown in detail the unloader 40 for transferring the bundles of stacked blanks from the underfeed stacker 30 to the uprighter 50. The unloader 40 comprises a plurality of upright structural members 58 having horizontal channel members 57 secured thereto. The lower part of the unloader is supported on wheels 33 riding on the longitudinal (with respect to the underfeed stacker 30) horizontal channel members. This lower part carries the backstop 34 and may be moved toward or away from the underfeed stacker as required by the lengths of the blanks 26ae being handled. The lower part has a network of horizontal structural members (FIG. 3) forming substantially a rectangle. The network is supported near each corner by plates 46 connected between the outermost of the longitudinal (with respect to flow of bundles from the underfeed stacker 30) structural members 65 and a pair of axles 59, one at each end of the network. The axles are connected to the wheels 33.

As previously noted, the underfeed stacker is provided with a backstop 34 which cooperates with the undenfeed stacker 30 to stack the blanks into bundles. The backstop 34 has an upper portion 35 and a lower portion 36. Each of the portions 35 and 36 has vertically extending spaced apart fingers 55 and 56, respectively, which interlace when the backstop is closed. Each set of fingers 5'5 and 56 is capable by itself of preventing the flow of bundles.

The lower portion 36 is designed to be moved downwardly below the plane in which the stacked bundles are traveling to permit the bundles to move over the top of the fingers 56. The lower portion :36 comprises a transverse channel member 38 having attached at either end thereof a downwardly extending rack member 69. Each of the rack members 3 9 is maintained in slidable engagement with a U-shaped member 42 and is held in position therewith by one leg of an angle 44. Each of the 'U- shaped members 42 and each of the angles 44 is supported by the plates 46, one of which is positioned just past each end of the channel member 38. Operatively engaged with each of the rack members 39 is a gear 48. The gears 48 are connected for rotation with a common shaft 49 which is supported at either end to the plate 46 by pillow block bearings (not shown). Also connected to and supported by the plates 46 is a second channel member 52 which supports a bracket 53, having a fluid pressure cylinder 54 pivotally connected thereto. The cylinder 54 operates to reciprocally move a piston rod 47 extending from one end. There is provided a yoke 51 having one end rigidly secured to the shaft 49 and the other end pivotally connected to the free end of the piston rod 47. Refraction or extension of the rod 47 by the cylinder 54 causes the shaft and thus the gears 48 to rotate. Such rotation in turn either lowers or raises the rack members 39 and the channel member 38 connected thereto. Thus, as may be seen in FIG. 2, retraction of the rod rotates the gears 48 counterclockwise, thereby causing the lower portion 36 of the backstop 34 to be lowered.

As previously noted, the lower portion 36 is provided with vertical fingers 56. These are connected to the channel member 38 and extend upwardly therefrom. As will become clear from the description of the operation, it is these fingers 56 which serve to initially stop the beingstacked bundles from the underfeed stacker.

In contrast to the lower portion 36 moving downwardly, the upper portion 35 is designed to move horizontally with the stacked bundles away from the undenfeed stac er 30. The upper portion 35 comprises a transversely disposed angle member 37 supported at each end on a movable carriage 61. Finge-rs 55 (FIG. 4) are secured to and extend downwardly from angle member 37. The fingers 55 are so spaced with respect to the fingers 56 of the lower portion 36 that the respective sets of fingers will be interlaced when the carriage 61 is forward and the lower portion 36 -is raised. The carriage 61 is supported on a pair of transversely disposed axles 63, each of which has wheels 62 connected to either end by means of bushings 66. The wheels 62 ride on the outer of the longitudinal structural members 65. The carriage 61 has a cam 41 connected thereto. The cam engages a limit switch 248 when the carniage 61 is in its forward position and engages an actuating lever of an exhaust valve 251 when the carriage is in its rearmost position. The function of the switch and the exhaust valve will become apparent from the description of the pneumatic system which will follow subsequently.

At the end of the unloader 40 away from the underfeed stacker 30 there is provided power means including an air motor 69 having a gear reduce-r 71 connected thereto by means of a coupling 68. The motor 69 and gear reducer 7 1 may be supported by any desired means to the structural network of the unloader. The air motor is operated by pressured air flowing through one of the lines 216, 21 3 connected thereto. The direction of rotation of the air motor may be varied by alternating the air flow from one line to the other.

A pair of sprockets 73 are positioned one on each side of the gear reducer 71. Each of the sprockets 73 has a stub shaft 74 connected to the gear reducer by coupling 72. The stub shafts 74 are secured to the outer structural members 65 by means of bearings 67. One of the stub shafts 74 (the left one in FIG. 5) is provided with an extension 74a having a pinion gear 102 mounted for rotation therewith. The pinion 102 engages a gear 103 of a single port exhaust valve 227. Exhaust from the air motor 69 is directed through said valve 227 during that phase of the cycle when the air motor is receiving pressured air through line 218 and exhausting it through line 216 so that it is rota-ting to carry .the carriage 61 toward the underfeed stacker 30. When the cycle is reversed, so that the carriage is being carried away from the underfeed stacker, exhaust from the air motor 69 is directed through valve 251. This will be covered more fully in the description of the pneumatic system which will [follow subsequently.

At the underfeed stacker end of the unloader 40 are another pair of sprockets 75. The forward sprockets 75 are rotatably supported on a shaft 76 connected by means of a bearing (not shown) to the plate 46. Each of the forward sprockets 75 is aligned with one of the sprockets 73. Each of the respective sets of aligned sprockets 73 6 and has a chain 77 reeved therearound. The chains 77 are connected to the carriage 61. Accordingly, movement of the chain 77 causes the carriage 61 and thus the upper portion 35 of the backstop to move. 'Each of the chains 77 has support wheels 78 spaced periodically therearound. These support wheels 78 when in the upper half of the cycle, are adapted to ride upon the outer structural members 65. As a result, the wheels 78 serve to support the upper reach of the chain in substantially a horizontal plane. There are provided a plurality of laterally extending supporting bars 79 which are connected to and supported by oppositely aligned wheels 78 of the respective chains 77. The purpose of these supporting bars 79 is to support the stacked bundles during their movement through the unloader. Accordingly, bars 79 are provided for only one-half of the loop defined by the endless chains 77. As shown in FIG. 2, when the carriage 6'1 and the upper portion 35 of the backstop are forward (toward the underfeed stacker 30), the bars 79 are positioned on the lower reach of the chains '77. Rotation of the sprockets 75 in a counterclockwise direction moves the upper port-ion 35 of the backstop 34 and the stacked bundles onto the unloader 40 (provided, of course, the lower portion of the backstop is down). The bars 79 travel around the sprockets 75 to the upper reach of the chains 77 where they successively engage and support said bundles.

The upper part of the unloader 40 has a network of upper structural members 83 supported on the upright structural members 58 above the upper portion 35 of the backstop 34 a sufiicient distance that it will not interfere with the movement of said upper portion on the carriage 61. The upper structural members 83 carry a pair of parallel channel members 84 which extend transversely of the direction of travel of the carriage 61. Each of the channels 84 has an angle member 85 secured thereto. A pair of shafts 86 extends between the angle members 85 and have wheels 87 on each end which ride on the upper face of the angle members. Secured to the shafts 86 is a dolly 88 carrying a pusher plate 89. Near each end of the channel members 84 there is provided a shaft 91 which spans the distance between the respective channel members 84 and which is supported in bearings 92. Each shaft has a pair of sprockets 93 secured thereto. A pair of chains 94 are reeved around the respective pairs of aligned sprockets 93 in a conventional fashion. The dolly 88 is connected to each of the chains 94 so that movement of the chain causes the dolly and the pusher plate to move and thereby push the group of bundles (five bundles by virtue of the number of slitters shown in FIG. 1) off of the bars 79 of the unloader 40 onto the upri-ghter 50.

Power to move the chain is provided by an air motor 95 connected to a gear reducer 96 by means of a coupling 98. The gear reducer 96 is connected to an extension 91a of the forward (with respect to the uprighter) of the shafts 91. The forward of the shafts 91 also has another extension 91b having a pinion gear 99 secured for rotation therewith. The pinion gear 99 engages a gear 101 of a double port exhaust valve 243. Exhaust from air motor 95 is directed through the exhaust valve 243.

Uprighter Referring now to FIGS. 6-10, the uprighter 50 comprises a plurality of vertical supporting members having connected thereto a network of horizontal supporting members 111. There is provided a plurality of con tinuously moving conveyor belts 112 reeved around pulleys 113 at either end of the upri ghter 50. The upper portion of the belts 112 ride upon the surface of the horizontal supporting members 111 to provide a fiat surface on which the bundles may be conveyed. The pulleys 113 furthest removed from the unloader 40 are mounted for rotation with shaft which extends laterally of the uprighter. The shaft 120 rotates in bearing blocks 121 which are secured to the structural members by any desired means. The pulleys 113 at the end of the uprighter near the unloader are mounted on individual stub shafts 124. The shafts 124 are supported in one end of arms 122. The other end of the arms 122 are pivotally connected to one of the structural members. An expandable bolt 123 is positioned between the structural members and the center of each of the arms 122. Any slack in the belts 112 may be taken up by expanding the bolts 123 to move the pulleys 113 at the unloader end of the uprighter away from the pulleys at the other end.

Rotation of the shafts 120 is powered by means of a motor 114 connected by means of a coupling 124 to a gear reducer 115. The gear reducer has a sprocket 116 connected to the shaft thereof. A chain 118 is reeved around the sprocket 116 of the gear reducer and a second sprocket 117 which is connected to the shaft 120 (see FIGS. 7 and 8). The motor 114 operates to continuously move the belts 112 during operation of the sheet handling apparatus.

Near the end of the conveyor belts 112 there is provided mechanism for turning individual stacked bundles so that each of the slitted blanks of cardboard rests upon its longitudinal edge. The mechanism includes a laterally extending shaft 132 supported on bearings 131 which lie in a plane slightly below the upper surface of the conveyor belts 112. Secured to the shaft 132 are a plurality of shaped plates 133 mounted on hubs 134. Each of the plates is formed with four arms 135 at right angles to one another. A single stacked bundle is moved by the conveyor belts until it overlies the upper edge of the forward horizontal arm and continues until it contacts the forward edge of the vertical arm which prevents further movement of the bundle. The shaft and thus the plate is then caused, by means hereinafter described, to rotate in a counterclockwise direction as viewed in FIG. 7, thereby turning said bundle so that the individual blanks thereof rest on their respective longitudinal edges. To hold the sheets on edge, each of the arms 135 is provided with an outwardly extending finger 136. If desired, a series of backstop plates 125 may be provided to assist in holding the blanks on edge.

Since the bundles are upended one at a time, it is obvious that no bundle should be moving into the arms 135 until the previous bundle has been upended and trailing finger 136 is out of the way. Mechanism is provided to insure that no bundles move into the arms 135 until the proper time. This mechanism includes a pair of gates 140 positioned between conveyor belts 112 and mounted for movement from a lowered position below the conveyor belts 112 to a raised position above the belts (FIGS. 7 and 9) where they act to prevent movement of any bundles. The gates 140 are supported by brackets 141 which are rigidly secured to a rotatable shaft 142. Partial rotation of the shaft to move the gates 140 between a raised and a lowered position is effected by means of a fluid pressure cylinder 144 having the free end of its piston rod pivotally connected to a crank 145 which is secured to the shaft 142. The cylinder 144 is pivotally supported by any desired means. The gates 140, when raised, prevent the movement of stacked bundles into the cross-arms 135 of the uprighter.

Lowering of the gates 140 by retraction of the cylinder permits stacked blanks to enter the cross-arms. However, as previously noted, inasmuch as the bundles are turned so that the individual sheets rest on their respective edges, it is necessary that only a single stacked bundle of the group (five as previously described) be permitted to enter the cross-arms of the uprighter at a time, and that the other bundles in the group be held back until the first bundle has been turned. Mechanism for holding back the trailing bundles is hereinafter described.

Referring particularly to FIGS. 6, 7, and 10, the mechanism for insuring that only a .single stacked bundle is moved into the cross-arms 135 when the gate 140 is lowered includes a plurality of longitudinally extending bars 146, one positioned beside each of the conveyor belts 112 parallel thereto. The bars are mounted for movement between a raised position above the surface of the conveyor belts and a lowered position below the surface of the conveyor belts. Each of the bars 146 is supported near its ends on a pair of parallel motion arms 147. The rearmost (toward unloader 40) of the parallel motion bars 147 are pivotally supported to any desired structural member. The parallel motion arms 147 located near the forward end of the bars 146 are rigidly secured to a rotatable shaft 148. The shaft 148 is supported "by bearing blocks 151 secured to one of the horizontal structural members. Partial rotation of the shaft 148 is effected by means of a fluid pressure cylinder 150 having the free end of its piston rod pivotally connected to a crank 149 which is rigidly secured to the rotatable shaft 148. For the stage of the operation as shown in FIG. 7 the parallel motion arms 147 are angled slightly forward so that the bars 146 are lowered with their top'surfaces lying below the plane of the conveyor belts 112. Activation of the cylinder 150 causes its piston rod to extend against the crank 149, thereby partially rotating the shaft 148 in a clockwise direction. This causes the parallel motion arms 147 to move from their angled forward position of FIG. 7 to a nearly vertical position, thereby raising the bars 146 so that their upper surfaces lie in a plane which is higher than that of the conveyor belts 112. In this manner any bundles beneath the bars 146 are prevented from moving forward even through the gate 140 is lowered and the belts 112 continue to move. As will become apparent from description of the pneumatic system, the operation of the gates 140 and the bars 146 is so synchronized that the bars are lowered when the gates are raised and vice versa.

As previously noted, it is desired that a single stacked bundle enter the cross-arms upon lowering of the gate 140. Inasmuch as the widths of the bundles may vary depending on the spacing between the slitters 19ae (FIG. 1), it is necessary that the distance between the raised gates and the leading edge of the bars 146 be substantially the width of a single bundle. The apparatus of the present invention is adapted to process bundles of varying widths; accordingly, there is provided means for adjusting this distance (see FIG. 10). Each of the bars 146 is provided with an extension 152 operably engaged therewith for raising and lowering with the bar 146. The extension 152 comprises an inverted T-mernher 153 positioned so that its upper surface is in the same plane as the upper edge of the bars 146. The inverted T-member 153 is held in position by a pair of plates 160, one on each side of the upright portion thereof (see also FIG. 6). Secured to the lower face of the inverted T-member 153 is a rack member 154. The rack 154 is engaged by a pinion gear 155 secured to a rotatable shaft 156. Rotation of the pinion gear 155 by means of shaft 156 extends or retracts the inverted T- member depending on direction of rotation. A manually rotatable wheel 157 is connected to the shaft 156 by means of a pair of stub shafts 158 and a pair of knuckle couplings 159. The outer stub shaft 158 is supported on one of the structural members by any desired means. The knuckle coupling connection between the wheel 157 and the shaft 156 permits the required movement of the shaft 156 when the parallel motion arms 147 are moved.

After a single stacked bundle has entered the crossarms 135, it is upended by rotating the shaft 132 carrying the plates 133 and their respective cross-arms 135 90 Mechanism for accomplishing such rotation includes a drive plate 162 mounted on one end of the shaft 132. The drive plate 162 has four holes 16311-11 spaced at 90 intervals near the periphery of the plate. J uxtapositioned with the inside face of the drive plate is a quadrant member 161. The quadrant member has a substantially 90 pie-shaped configuration and has gear teeth around its arcuate edge. The quadrant is supported on the hub of the drive plate 162 and may rotate thereon (see FIG. 9). There is provided a rack member 164 having teeth adapted to engage the teeth of the quadrant 161. Movement of the rack is effected by a fluid pressure cylinder 166 having the free end of its piston rod connected thereto. Vertical support for the rack is provided by a support member 165 upon which the rack rides. A housing 171 secured to the quadrant 161 carries a spring loaded pin 167 which is adapted to successively engage each of the holes 163ad of the drive plate 162. The spring acts to urge the pin 167 outwardly so that it normally engages one of the holes 163a-d. Thus, in FIG. 9 the pin 167 is engaging the lower hole 163a. The pin 167 initially became engaged with its present hole 163a when it was 90 away, where hole 163d (FIG. 7) is presently located. At that time the rack was extended. Retraction of the rack 164 by the cylinder 166 caused the quadrant 161 to rotate in a counterclockwise direction (as viewed in FIG. 7). By virtue of the fact that the pin 167 was engaged with the hole of the drive plate 162, the plate was also caused to rotate 90, as was the shaft 132 and the cross-arms carrying the single bundle. This in turn rotated the bundle so that the individual sheets thereof rest on their respective edges.

After the quadrant has been rotated 90 counterclockwise, it is necessary to disengage the pin 167 from the hole so that the rack 164 may be extended to rotate the quadrant clockwise without rotating the plate 162 and the shaft 132. To accomplish this there is provided a fluid pressure cylinder 169 carrying a lock pin 168 on the end thereof. The cylinder 169 is positioned so that the lock pin is aligned with the lower hole 163a of the plate 162. A limit switch 290 (FIG. 8) is positioned for engagement by a finger 170 extending from rack 164 upon completion of retraction of the rack 164. As will become clear from the description of the pneumatic system, this opens a valve 272 permitting pressured air to flow to the rear of cylinder 169 to thereby extend the lock pin 168 to push the pin 167 out of the hole of the drive plate 162. It is then possible for the rack to be extended, thereby moving the quadrant clockwise without causing rotation of the drive plate 162. Full extension of the rack 164 causes the pin 167 to become aligned with hole 163d where it is urged by the spring to engage said hole. The mechanism is now in position to again rotate the crossarms 135 upon retraction of the rack 164.

Near the end of the uprighter positioned above the belts 112 are a plurality of horizontal plates 173 to support the respective edge-turned blanks. A continuously rotating rubber surfaced wheel 174 is positioned between two of the plates 173 so that its upper surface is slightly above the upper surface of the plates. The rubber surfaced wheel thus engages the edges of the respective sheets and urges them laterally (to the left as viewed in FIG. 8) off the uprighter 50.

The wheel 174 is mounted on a shaft 177 supported by a pivoted bracket 178. Continuous rotation is effected by the pair of bevel gears 175, one connected to the continuously rotating shaft 120 carrying the pulleys of the conveyor belts 112 and the other connected to a shaft 180 having a sprocket 176 mounted thereon, The shaft 177 carrying the wheel 174 has a sprocket 137 secured to its end in alignment with sprocket 176. A chain 179 is reeved between the sprockets 137 and 176. Accordingly, continuous rotation of the shaft 120 causes continuous rotation of the wheel 174.

Thus, the edge-turned blanks are urged laterally off the uprighter 50 by continuous rotation of the wheel 174. However, complete movement off the uprighter is retarded by a gate 181 which serves to align the ends of the respective blanks. The gate 181 is mounted on the free end of the piston rod of a fluid pressure cylinder 182. A rod 126 having a finger 127 depending therefrom is mounted for movement with the piston rod of the 1t) cylinder 182. The finger 127 engages and thereby actuates one limit switch 270 when extended and another, 275, when retracted. There is provided a plate 183 connected to a pair of angle irons 184- to support the edge-turned sheets as they leave the uprighter. It is while the blanks are stopped by the gate 181 that they are engaged by the clamp 60.

Clamp The clamp 60, shown in detail in FIGS. 11 and 12, comprises a pair of arms 187 and 188 each carrying a bundle engaging plate 189 on the free end thereof. A fluid pressure cylinder 194 has one end rigidly connected to arm 188 and has the free end of its piston rod pivotally connected to arm 187. The cylinder 194 operates to extend its piston rod to close the clamp or retract the rod and open the clamp (shown in phantom lines in FIG. 11). Inasmuch as the cylinder 194 acts as a portion of one arm of the clamp, it, as well as the arm 187, must be free to pivot. Accordingly, the cylinder 194 is pivotally supported between one end of a pair of plates 193 and the arm 187 is pivotally supported between the other end. The plates 193 are supported on a dolly 191 adapted to move the clamp 60 from the uprighter 50 toward the saw 70. The dolly 191 is carried on wheels 197 which ride on the horizontal legs of the angle irons 184. The sides of the dolly have downwardly extending portions 192 to which the plates 193 are rigidly secured.

Means for moving the dolly 191 from the gate 181 toward the saw 70 include a telescoping bar 201 having one end pivotally connected to the dolly and the other end pivotally connected to the floor. A fluid pressure cylinder 202 (FIG. 9) has the free end of its piston rod pivotally connected to the bar 201. The cylinder 202 may be supported by any desired structural means. Extension of its piston rod by the cylinder 202 causes the bar 201 to pivot around its floor support so that the upper end carries the dolly 191 to the left as viewed in FIG. 9. By virtue of the fact that the bar 201 has telescoping sections, the end connected to the dolly 191 is permitted to remain in the plane determined by the horizontal legs of the angle irons even though it pivots around a fixed point at the other end.

A pair of limit switches 264 and 278 are mounted in the path of travel of the clamp 80. Switch 264 is engaged by the plate 193 as the dolly 191 reaches the end of its movement toward the uprighter 60. Switch 278 is engaged by the plate as the dolly reaches the end of its movement away from the uprighter. The effect of such engagement will become apparent from the descrip tion of the pneumatic system which follows.

Pneumatic system The apparatus of the present invention is provided with two pneumatic systems. The first handles the operation of the unloader 40, while the second handles the operation .of the uprighter 50 and the feeder clamps 60.

The pneumatic system for the unloader 40 comprises a control valve 206 for controlling the flow of pressured fluid to the fluid pressure cylinder 54 which controls the raising and lowering of the lower portion 36 of the back stop 34. The valve 206 receives pressured air from a supply source (not shown) and directs it either through line 207 to the rear of the cylinder 54 to cause the cylinder to extend its piston rod, or through line 208 to the forward end of such cylinder to cause it to retract its piston rod. The valve 206 has a solenoid 206a at one end which controls the opening of the port leading to line 208 and a second solenoid 20612 which controls the opening of the port to line 207. The solenoid 206a is actuated by an impulse received through wire 203. The impulse through wire 203 to open the port to line 208 is controlled by the counting means which measures the number of sheets flowing under the brackets 12 (FIG, 1). Impulse to the solenoid 206k to open the port leading 

